WO2013032431A1 - Ensemble moteur en x équilibré - Google Patents

Ensemble moteur en x équilibré Download PDF

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Publication number
WO2013032431A1
WO2013032431A1 PCT/US2011/049492 US2011049492W WO2013032431A1 WO 2013032431 A1 WO2013032431 A1 WO 2013032431A1 US 2011049492 W US2011049492 W US 2011049492W WO 2013032431 A1 WO2013032431 A1 WO 2013032431A1
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WO
WIPO (PCT)
Prior art keywords
crankshaft
crankpins
axis
engine
cylinder
Prior art date
Application number
PCT/US2011/049492
Other languages
English (en)
Inventor
Matthew B. Diggs
Original Assignee
Diggs Matthew B
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Diggs Matthew B filed Critical Diggs Matthew B
Priority to US13/521,312 priority Critical patent/US9051833B2/en
Priority to EP11752430.6A priority patent/EP2751390A1/fr
Priority to PCT/US2011/049492 priority patent/WO2013032431A1/fr
Publication of WO2013032431A1 publication Critical patent/WO2013032431A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F01B15/02—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 with reciprocating cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/16—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with pistons synchronously moving in tandem arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/227—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinder banks in X-arrangement, e.g. double-V engines

Definitions

  • the invention relates generally to internal combustion piston
  • the objective of an engine designer is to provide the best function with regards to performance and efficiency, while also minimizing the amount of noise and vibration that emanate from the engine. It is also desirable to provide an engine that is the smallest, lightest- weight while having a design which can be economically manufactured and serviced.
  • the Scotch yoke is a mechanism for converting the linear motion of a slider into rotational motion of a shaft or vice-versa, and has been demonstrated to be suitable for use in internal combustion piston engines.
  • the piston or other reciprocating part is directly coupled to a sliding yoke with a slot that engages a pin on the rotating crankshaft, with a bearing block is fitted in between the crankshaft and the yoke to provide a cylindrical-cylindrical interface at the crankpin and flat-on- flat interface with the yoke so that the contact pressures at both interfaces are at acceptable levels.
  • the shape of the motion of the piston is a pure sine wave over time given a constant rotational speed of the crankshaft.
  • the scotch yoke mechanism is a mechanism that couples the reciprocating pistons to the rotating crankshaft with true harmonic motion for the reciprocating mass, assuming a constant rotational speed of the crankshaft, such that an engine that uses scotch yokes can be said to be "100% balanced for all orders" or "perfectly balanced” if it is balanced for l st -order forces and moments.
  • the scotch yoke mechanism can be used in a double-ended or "double-acting" fashion such that each reciprocating assembly has a piston at either end, hence a benefit of the double-acting scotch yoke is that the fluid motion inside the crankcase is reduced because opposite pistons simply push air in between them, whereas in "V"-type engines and in-line engines there is a larger mass of fluid in motion inside the crankcase which is pushed out of the cylinders and around the engine's bulkheads in a way that causes larger amounts of fluid friction and necessitates having an empty volume in the engine crankcase to allow this fluid motion to occur. So, it can be seen that the Double -Acting Scotch Yoke system can provide an engine with reduced friction which translates to better fuel efficiency and better performance.
  • Double- Acting Scotch Yoke Another capability of the Double- Acting Scotch Yoke is that it can be used in an X-engine configuration having two reciprocating assemblies for a total of four pistons coupled to each crankpin bearing on the crankshaft in a similar way to the conventional connecting rod as it is used in V-configuration engines which have two con rod and piston assemblies coupled to each crankpin bearing on the crankshaft.
  • Double- Acting Scotch Yoke used in X-configuration can result in a significantly smaller and lower mass engine for a given bore & stroke and number of cylinders when compared with in-line, "V" and flat engine configurations.
  • a radial engine that employs a master con rod with secondary con rods attached to it is an arrangement which allows multiple cylinders of an engine to be attached to a single crankpin bearing, but the compromise here is that there are at least two different piston motions (piston displacement versus crankshaft angle) occurring in this type of engine, which greatly complicates any efforts to achieve balance of even the l st -order of vibration. Hence, there is no practical method to have 1 st and 2 nd order balance for a group of cylinders connected in this way.
  • An object of the invention is to provide a series of X-Engine configurations that achieve perfect balance - that is, zero vibrating forces or moments of any order (either l st -order, 2 nd -order or higher orders), and also have zero torsional loading on the crankshaft resulting from reciprocating masses. This is a better result than practically any engine in production today due to the fact that nearly all engines employ the connecting rod mechanism, which results in multiple orders of vibrating moments and forces and also torsional loading on the crankshaft for which there is no practical way to cancel or resolve.
  • the Double-Acting Scotch Yoke (DASY) X-Engine can be configured using a 90° X-angle such that a single-central crankshaft is surrounded by four banks of cylinders with all four banks of cylinders located on two planes which intersect at a 90° angle with the crankshaft axis on the line of intersection, and having the engine configured so that there are two reciprocating DASY assemblies with two pairs of opposing-pistons for a total of four pistons coupled to each crankpin on the crankshaft such that each crankpin is associated with a piston that is engaged with one cylinder of each of the four cylinder banks, and having a bank offset such that the two DASY assemblies coupled to each crankpin are offset along the axis of the crankshaft.
  • the total number of cylinders is four times the number of crankpins. Perfect balance for some of these configurations is achieved inherently - that is, without the use of an extra balancing mechanism - by having the crankpins on the crankshaft in specific angular relations to one another. While having inherent balance, it will be shown that these configurations also achieve even-firing for either 4-stroke or 2- stroke or other engine cycles.
  • a DASY X-Engine can be configured as just described, except having the crankpins on the crankshaft in any angular relation to one another, thus being able to satisfy more even-firing engines with the 4-stroke, 2-stroke or other engine cycles, and having a single counter-rotating l st -order moment- balance shaft mounted on the engine structure in parallel to the crankshaft axis which, in every case, results in perfect balance.
  • the total number of cylinders is four times the number of crankpins.
  • Packaging of the balance shaft is made relatively simple due to the engine structure having four "valleys" between the four cylinder banks around the periphery of the engine each of which are suitable for mounting a balance shaft.
  • the DASY X-Engine can be configured using a
  • crankshaft configured so that there is one reciprocating DASY assembly with two opposing pistons coupled to each crankpin on the crankshaft, thus also being able to satisfy more even- firing engines with the 4- stroke, 2-stroke or other engine cycles.
  • the total number of cylinders is two times the number of crankpins. Perfect balance of these configurations can be achieved by having the crankpins on the crankshaft in specific angular relations to one another and having a single counter-rotating l st -order moment-balance shaft mounted on the engine structure in parallel to the crankshaft axis.
  • the Double- Acting Scotch Yoke (DASY) X- Engine can be configured using a non-90 0 X-angle such that there is the same less-than-90 0 angle between adjacent cylinder banks in two opposite corners, and the same more-than-90° angle between adjacent cylinder banks in the other two opposite corners, and having a crankshaft configured so that there is one or two reciprocating DASY assemblies coupled to each crankpin on the crankshaft.
  • the balance comprises four cylinder banks arranged around a central crankshaft, the cylinder banks lying in two intersecting planes with a crankshaft axis being on a line which is the intersection of the two planes.
  • the same number of cylinders are on each cylinder bank.
  • the crankshaft has one or more crankpins, with each crankpin having one or more reciprocating assemblies coupled to it.
  • the reciprocating assemblies are offset relative to each other along the crankshaft axis.
  • Each reciprocating assembly is coupled to a crankpin on the crankshaft in such a way that, as the crankshaft rotates, the reciprocating assembly moves in reciprocating-linear motion.
  • An outward- facing piston is at both ends of each reciprocating assembly with each piston coaxially engaged with a cylinder of a cylinder bank.
  • the two outward-facing pistons of each reciprocating assembly are coaxial with the axis of the pistons and being perpendicular to the crankshaft axis.
  • FIG. 1 is an isometric view of the DASY X-4 engine crank train which includes one crankshaft and four pistons (for FIGS. 1, 2, 3 (a)-(b)) the crankshaft does not include counterweights to allow viewing of the parts);
  • FIG. 2 is an exploded view of the DASY X-4 engine crank train of FIG. 1 including two DASY assemblies (one in exploded view), two bearing block assemblies (one in exploded view) and a crankshaft according to an embodiment of the invention;
  • FIGS. 3(a) and 3(b) are side and top views, respectively, of the DASY X-4 engine crank train of FIG. 1;
  • FIGS. 4(a) and 4(b) are a top view and side view, respectively, of the crankshaft (including counterweights) shown in FIGS. 1-3;
  • FIG. 4(c) is an exploded view of the X-4 crank train including the crankshaft, two DASY assemblies, and two bearing block assemblies;
  • FIG 4(d) is an isometric view of the X-4 crank train when assembled
  • FIG. 5(a) is an isometric view of a crankshaft for the X-8 engine shown in FIG. 5(a);
  • FIG. 5(b) is a top-hidden-line view of the crankshaft (without counterweights) shown in FIG. 5(a);
  • FIG. 5(c) is an isometric view of the X-8 crank train for even-firing 4-stroke cycle with X-Y-Z coordinates used in the balance calculation analysis;
  • FIG. 5(d) is an isometric view of the X-8 engine bottom end assembly showing the four cylinder banks of an X-engine;
  • FIG. 6(a-e) are graphical representations of the balance calculation results for the X-8 configuration for 4-stroke cycle.
  • forces in the x-direction forces in the y-direction, moments about the y- axis, moments about the x-axis, moments about the z-axis which are the torsional loads on the crankshaft due to reciprocating masses.
  • NOTE all figures which have balance calculation results are configured the same as FIGS. 6(a-e));
  • FIG. 7(a) is an isometric view of a crankshaft for the X-12 engine for even-firing 2-stroke cycle
  • FIG. 7(b) is a top-hidden-line view of the crankshaft (without counterweights) shown in FIG. 7(a);
  • FIG. 7(c) is an isometric view of the X-12 crank train for even- firing 2-stroke cycle with X-Y-Z coordinates used in the balance calculation analysis;
  • FIGS. 8(a-e) are graphical representations of the balance calculation results for the X-12 configuration for even-firing 2- stroke cycle;
  • FIG. 9(a) is an isometric view of a crankshaft for the X-16 engine for even-firing 4-stroke cycle
  • FIG. 9(b) is an isometric view of the X-16 crank train for even- firing 4-stroke cycle with X-Y-Z coordinates used in the balance calculation analysis;
  • FIG. 9(c) is a top-hidden-line view of the crankshaft (without
  • FIGS. 10(a-e) are graphical representations of the balance
  • FIG. 11(a) is an isometric view of a crankshaft for the 2-stroke X-4;
  • FIG. 11(b) is an isometric view of the X-4 (2-stroke) crank train with X-Y-Z coordinates used in the balance calculation analysis;
  • FIGS. 12(a-e) are graphical representations of the balance
  • FIG. 13(a) is an isometric view of a crankshaft for the X-12 engine for even-firing 4-stroke cycle
  • FIG. 13(b) is an isometric view of the X-12 crank train for even- firing 4-stroke cycle with X-Y-Z coordinates used in the balance calculation analysis;
  • FIG. 13(c) is a top-hidden-line view of the crankshaft (without counterweights) shown in FIG. 13(a);
  • FIGS. 14(a-e) are graphical representations of the balance
  • FIG. 15(a) is an isometric view of a crankshaft for the X-8 engine for even-firing 2-stroke cycle
  • FIG. 15(b) is an isometric view of the X-8 crank train for even- firing 2-stroke cycle with X-Y-Z coordinates used in the balance calculation analysis
  • FIG. 15(c) is a top-hidden-line view of the crankshaft (without counterweights) shown in FIG. 15(a);
  • FIGS. 16(a-e) are graphical representations of the balance
  • FIG. 17(a) is an isometric view of a crankshaft for the X-8 engine with a 75° X-angle for even- firing 4-stroke cycle;
  • FIG. 17(b) is a top-hidden-line view of the crankshaft (without counterweights) shown in 17(a);
  • FIG. 17(c) is a top-view of the X-8 crank train for even- firing 4- stroke cycle with a 75° X-angle;
  • FIG. 17(d) is a top-view of the 75° X-8 engine bottom end
  • FIG. 18(a) is an isometric view of the X-8 crank train for the X-8 engine with a 75° X-angle for even-firing 4-stroke cycle with X-Y- Z coordinates used in the balance calculation analysis;
  • FIG. 18(b) is an isometric view of the 75° X-8 engine bottom end assembly
  • FIG. 18(c) is an isometric view of a crankshaft for the X-12 engine with a 75° X-angle for even- firing 4-stroke cycle;
  • FIG 18(d) is a top-hidden-line view of the crankshaft (without counterweights) shown in FIG. 18(c);
  • FIGS. 19(a-e) are graphical representations of the balance
  • FIGS. 20(a-e) are graphical representations of the balance
  • a Double-Acting Scotch Yoke (DASY) X-Engine crank train 10 is shown according to an embodiment of the invention.
  • the crank train 10 includes two DASY assemblies 12, two bearing block assemblies 14 and a crankshaft 16.
  • the X-engine crank train 10 is configured as a DASY X-4 crank train.
  • the DASY X-4 crank train 10 can be grouped together in multiples to form other X-engine systems, such as a X-8 engine crank train, a X-12 engine crank train, a X-16 engine crank train, and the like.
  • the DASY assembly 12 forms a basic building block of the DASY X-engine crank train 10 and comprises four components joined together in series:
  • first piston 18 is identical to the second piston 28, and the first yoke 22 is identical to the second yoke 24.
  • the yokes 22, 24 are rigidly connected to each other by using a pair of threaded fasteners 25, such as bolts, and the like, that are passed through a non-threaded hole 27 in one leg 21 of the yoke 22, 24 and received in a threaded hole 31 in the leg 23 of the other yoke 22, 24, as shown in FIG. 4.
  • a dowel 29 is positioned within a separate countersunk bore (not shown) that can be on-axis with holes 27, 31 or can be offset from the axis of the holes 27, 31.
  • each leg 21, 23 of each yoke 22, 24 has a planar end surface 35 that forms a flat-to-flat interface between the two yokes 22, 24 when assembled. That is, each yoke 22, 24 has two planar end surfaces 35 that form a flat-to- flat interface between the two yokes 22, 24.
  • the yokes 22, 24 are identical to each other so that the same part can be used on both sides of the bearing block assembly 14 by rotating one of the yokes 180° with respect to the other yoke, which results in a reduction of different parts necessary in the assembly 12.
  • One aspect of the invention is that the yokes 22 24, the dowels 29, the threaded fasteners 25 and the pistons 18, 28 of the DASY assembly 12 in a purely symmetrical relation to a common, center axis 33 of the two opposing pistons 18, 28, and the common, center axis 33 of the two opposing pistons 18, 28 is perpendicular to a center axis 30 of the crankshaft 16 in the assembled X-engine configuration, as shown in FIG. 3.
  • This feature enables the center- of-mass of the DASY assembly 12 to be located on the common, center axis 33 of the two opposing pistons 18, 28, which is desirable in order to achieve balance of reciprocating and rotating masses during operation of the X-engine.
  • each piston 18, 28 includes a combustion face 62 on its end, which is formed to suit the requirements of the combustion process being used.
  • each bearing block assembly 14 includes two identical bearing block halves 42, 44 and capture a pair of 180° bearing shells 46, 48 that surround the crankpin 32 in a slideable, rotatable manner.
  • a plurality of threaded fasteners 50 such as bolts, and the like, hold the bearing block assembly 14 together.
  • the two bearing block assemblies 14 are assembled around the crankpin 32 of the crankshaft 16.
  • Each bearing block assembly 14 is coupled to its respective DASY assembly 12 by two linear bearing surfaces 34, 36 located at opposing ends of the bearing block assembly 14.
  • the crankshaft 16 has its main bearings 38, 40 positioned on the center axis 30 of the crankshaft 16 so that as the crankshaft 16 rotates, the crankpin 32 is rotating around the center axis 30 of the crankshaft 16 in an eccentric fashion.
  • FIGS. 1, 2 and 3(a, b) there are two bearing block assemblies 14 disposed about the crankpin 32 of the crankshaft 16 with each bearing block assembly 14 axially separated from one another and occupying a space along the outer surface of the crankpin 32 and each facing in a different orientation. Specifically, the two bearing block assemblies 14 are oriented 90° with respect to each other.
  • FIG. 3(a) is a side-view of the DASY X-4 crank train 10 with the axis 33 of one DASY assembly 12 shown with an offset 58 relative to the axis 33 of the other DASY assembly. This offset 58 is along the axis 30 of the crankshaft 16.
  • the X-4 crank train is shown in top view to reveal a right-angle relation of the two DASY center axes 33 which both intersect the axis of the crankshaft 30.
  • the interface between the DASY assembly 12 and the bearing block assembly 14 are two flat-to-flat sliding interfaces (i.e., linear bearing surface 34 contacts yoke 24, and linear bearing surface 36 contacts yoke 22) that are perpendicular to the common, center axis 33 of the two opposing pistons 18, 28.
  • the two bearing block assemblies 14 surround and engage the crankpin 32 of the crankshaft 16 and revolve, but do not rotate, around the center axis 30 of the crankshaft 16 as the crankshaft 16 rotates.
  • Each DASY assembly 12 is coupled to the bearing block assembly 14 in such a way that rotating motion of the crankshaft 16 is translated to a reciprocating (pure sinusoidal) motion of the DASY assemblies 12.
  • the two DASY reciprocating assemblies 12 are mounted transversely with respect to the crankshaft axis 30 which results in having the motion of the two DASY assemblies 12 being 90° out of phase with respect to each other, so for the X-4 crank train 10 one piston crosses through top-center position for every 90° of crankshaft 16 rotation.
  • the motion of the DASY assembly 12 is reciprocating harmonic (sinusoidal) motion. The result is:
  • crank radius stroke/2
  • crankshaft assembly 416 has counterweights 71 attached to the X-4 crankshaft section 16.
  • the crankshaft assembly 416 is designed so that it's mass (consisting of the crankshaft 16, counterweights 71 and including fasteners, etc.), and the distance to the center of mass 72, represented by "x-bar" in the equation, are such that the above equation is satisfied which results in having the rotating forces of the crankshaft perfectly cancel out the forces from the two reciprocating DASY assemblies 12 and the two bearing block assemblies 14.
  • crankshaft assembly 416 shown has bolted-on counterweights, whereas it is also possible to have single piece crankshafts with integral counterweights.
  • FIGS. 12(a, b) are exploded and assembly views of the balanced X-4 group 11 , showing all the components which must have the specific mass relationship as defined in the above equation in order to achieve force balance.
  • An analysis of the force balance for the balanced X-4 group 11 is shown graphically in FIGS. 12(a, b).
  • bearing block mass 0.451kg
  • crankshaft rotation clockwise (looking down z-axis)
  • crankshaft rotates with constant angular velocity, and the direction of rotation for the crankshaft is clockwise looking down the z-axis.
  • the first four cylinders #l-#4 are the top X-4 group of the engine and correspond to banks 151-154, respectively, as shown in FIG. 5(d).
  • the X-Y-Z coordinate system used for each analysis is placed on the crankshaft axis 30 at the center of the uppermost main bearing such that all of the cylinder axes are below the X-Y plane. DASYs with odd numbered cylinders are always parallel to the x-axis.
  • DASY 1-3 indicates the DASY that engages cylinders #1 and #3, which are on banks 151, 153 in FIG. 5(d).
  • the horizontal axis for all graphs is crank angle degrees from 0° to 360° which covers a full revolution of the crankshaft.
  • the piston for cylinder #1 is at top-center at 0° with respect to the balance calculation.
  • the terms “Fx crkshft” and “Fy crkshft” represent the combined rotating forces of the crankshaft and all of the bearing blocks connected to it resolved to the x and y directions
  • the terms “Mx crankshaft” (or “Mx crkshaft”) and “My crankshaft” (or “My crkshaft”) represent the combined rotating moments again including the crankshaft and all the bearing blocks connected to it resolved to the two axes x and y.
  • crankshaft as defined here uses the same counterweight configuration adjacent to each crankpin, whereas it is possible to configure the crankshaft counterweights in an infinite number of ways and still achieve the necessary balancing effect for rotating forces and moments.
  • the balance shaft is realized to have counter-rotating synchronized motion relative to the crankshaft, rotates at crankshaft speed, and generates a rotating moment.
  • FIGS. 5(a)-(d) The DASY X-8 configuration for even-firing 4-stroke cycle is shown in FIGS. 5(a)-(d).
  • FIG. 5(a) is the crankshaft 116 which has two crankpins 141, 142
  • FIG. 5(b) is a top-hidden-line view of the crankshaft (without the counterweights) showing that the two crankpins 141, 142 are arranged 180° opposed relative to the crankshaft centerline 30
  • FIG. 5(c) has a view of the X-8 (4- stroke) crank train 100 showing the X-Y-Z coordinate system used in the balance calculation.
  • FIG. 5(a) is the crankshaft 116 which has two crankpins 141, 142
  • FIG. 5(b) is a top-hidden-line view of the crankshaft (without the counterweights) showing that the two crankpins 141, 142 are arranged 180° opposed relative to the crankshaft centerline 30
  • 5(d) is a view of the engine bottom end assembly 160 which has four banks of cylinders 151, 152, 153, 154, which are arranged in "X" configuration around the main axis of the engine 190, with two cylinders 80 on each bank of cylinders 151, 152, 153, 154.
  • the crankshaft axis 30 is on line with the engine main axis 190 in the engine bottom end assembly 160.
  • crankshaft axis 30 results in the crankshaft being balanced for forces, but generating a rotating couple as the crankshaft rotates. This rotating couple, it will be seen, acts to cancel out the resultant vibration moments generated by the reciprocating DASY assemblies 12.
  • having the two crankpins 141, 142 arranged in this way results in having two pistons 18, 28 coming to top-center for every 90° of rotation of the crankshaft - a condition which is necessary for achieving an even-firing 4-stroke eight- cylinder engine.
  • the upper crankpin 141 has two reciprocating assemblies coupled to it to engage a cylinder on each of the four banks 151, 152, 153, 154, which are numbered cylinders #1, #2, #3, #4 corresponding to the cylinder banks 151, 152, 153, 154, respectively, and the second (lower) crankpin 142 is associated with the lower four cylinders numbered #5, #6, #7, #8 associated with the four cylinder banks in the same way.
  • the DASY assembly 12 that engages opposing cylinders 1 and 3 is referred to "DASY 1-3" in the analysis results.
  • DASYs with odd cylinder numbers are moving parallel to the x-axis
  • DASYs with even cylinder numbers are moving parallel to the y-axis.
  • FIGS. 6(a) With regards to moments about the y-axis and the x-axis, in FIGS.
  • FIG 6(e) the moment loading on the crankshaft as a result of the reciprocating DASY masses acting on the crankpin as it moves out of alignment with the centerline of the DASY 33 is shown.
  • DASY X-8 (4-stroke) engine can be made to fire evenly using any of four different crankshaft configurations - 0°-0°, 0°-90°, 0°-180°, 0°-270° - only the 0°-180° crankshaft configuration as shown in FIGS. 5(a,_b) provides perfect balance inherently, while the other three configurations - 0°-0°, 0°-90°, 0°-270° - would each require a balance shaft to achieve perfect balance.
  • FIGS. 7(a-c) The DASY X-12 configuration for even- firing 2-stroke cycle is shown in FIGS. 7(a-c).
  • FIG. 7(a) is the crankshaft 216, which has three crankpins 241, 242, 243 which are arranged 120° relative to each other about the axis of the crankshaft 30, and in FIG. 7(b) is a top-hidden-line view of the crankshaft (without the counterweights) showing the angle 275 being 120° angle between pins 241 and 243, and
  • FIG. 7(c) has a view of the X-12 (2-stroke) crank train 200 showing the X-Y-Z coordinate system used in the balance calculation.
  • the engine bottom end assembly is similar to that shown in FIG. 5(d), except that there are three cylinders 80 on each of four banks of cylinders 151, 152, 153, 154.
  • crankpins 241, 242, 243 arranged with a 120° mutual angular spacing results in having the crankshaft 216 being balanced for forces, but generating a rotating couple as the crankshaft rotates. This rotating couple, it will be seen, acts to cancel out the resultant vibration moments generated by the reciprocating DASY assemblies 12.
  • having the three crankpins 241, 242, 243 arranged in this way results in having one piston 18, 28 coming to top-center for every 30° of rotation of the crankshaft - a condition which is necessary for achieving an even- firing 2-stroke 12-cylinder engine.
  • the upper crankpin 241 has two reciprocating assemblies coupled to it to engage a cylinder on each of the four banks, which are numbered cylinders #1, #2, #3, #4 corresponding to the cylinder banks 151, 152, 153, 154, respectively, and the two lower crankpins 242, 243 are associated with the second and third groups of four cylinders numbered #5, #6, #7, #8, and #9, #10, #11, #12, respectively.
  • FIGS. 8(a)-(e) the balance calculation analytical results for the X-12 engine crank train for even- firing 2-stroke cycle are shown.
  • FIGS. 8(a)-(e) the balance calculation analytical results for the X-12 engine crank train for even- firing 2-stroke cycle are shown.
  • the DASY X-12 (2-stroke) is perfectly balanced inherently (with no balancing mechanisms used) and has zero torsional loads on the crankshaft from reciprocating masses.
  • FIGS. 9(a)-(c) The DASY X-16 configuration for even- firing 4-stroke cycle is shown in FIGS. 9(a)-(c).
  • FIG. 9(a) shows the crankshaft 316 that has four crankpins 341, 342, 343, 344
  • FIG. 9(b) is a view of the X-16 (4-stroke) crank train 300 showing the X-Y-Z coordinate system used in the balance calculation
  • FIG.9(c) is a top- hidden-line view of the crankshaft (without the counterweights) showing that the four crankpins 341, 342, 343, 344, are arranged in two pairs of 180°-opposed crankpins with the two opposed pairs of pins lying in planes which are 45° offset about the crankshaft axis 30, with crankpins 341 and 342 making one opposed pair, and crankpins 343 and 344 the other, and with angle 375 between the planes of the two pairs of opposed-crankpins being 45°.
  • the engine bottom end assembly is similar to
  • crankpins 341, 342, 343, 344 arranged as two pairs of 180°-opposed crankpins about the crankshaft axis 30 results in the crankshaft 316 being balanced for forces, but generating a rotating couple as the crankshaft rotates. This rotating couple, it will be seen, acts to cancel out the resultant vibration moments generated by the reciprocating DASY assemblies 12.
  • having the four crankpins 341, 342, 343, 344 arranged in this way results in having two pistons 18, 28 coming to top-center for every 45° of rotation of the crankshaft - a condition which is necessary for achieving an even-firing 4-stroke 16-cylinder engine.
  • the upper crankpin 341 has two reciprocating DASY assemblies 12 coupled to it to engage a cylinder on each of the four banks, which are numbered cylinders #1, #2, #3, #4 corresponding to the cylinder banks 151, 152, 153, 154 respectively, and in the same way the three lower crankpins 342, 343, 344 are associated with the second, third and fourth groups of four cylinders numbered #5, #6, #7, #8, and #9, #10, #11, #12, and #13, #14, #15, #16, respectively.
  • FIGS. 10(a)-(e) the balance calculation analytical results for the X-16 engine crank train for even- firing 4-stroke cycle are shown.
  • the DASY X-16 (4-stroke) is perfectly balanced inherently (with no balancing mechanisms used). While this embodiment defines one crankshaft configuration to achieve inherent perfect balance, there are 12 crankshaft configurations which can achieve inherent perfect balance and even-firing 4-stroke cycle, out of a total of 192 crankshaft configurations that have even-firing. There are 128 possible firing orders for each of the 12 crankshaft configurations for the even- fire 4-stroke X-16 with inherent perfect balance.
  • FIGS. 11(a) and (b) The DASY X-4 configuration for even- firing 2-stroke cycle is shown in FIGS. 11(a) and (b).
  • FIG. 11(a) the crankshaft 416 that has one crankpin 441 is shown
  • FIG. 11(b) is a view of the X-4 (2-stroke) crank train 400 showing the X-Y-Z coordinate system used in the balance calculation.
  • the engine bottom end assembly is similar to that shown in FIG. 5(d), except that there is one cylinder 80 on each of four banks of cylinders 151, 152, 153, 154.
  • the crankpin 441 has two reciprocating assemblies coupled to it to engage a cylinder on each of the four banks, which are numbered cylinders #1, #2, #3, #4 corresponding to the cylinder banks 151, 152, 153, 154, respectively. Having one crankpin 441 results in the crankshaft 416 having a rotating force as the crankshaft rotates 405 which acts to perfectly counter the inertia forces of the two DASY reciprocating mechanisms 12. However, there is a residual vibration for the crankshaft 416, two bearing blocks 14 and the two DASYs 12 which is a rotating moment that rotates in the opposite direction to the crankshaft. Hence, as shown in FIG.
  • a single counter-rotating l st -order moment-balance shaft 401 mounted in the engine structure on an axis parallel to the crankshaft axis 30, and rotates in the opposite direction 406 to the crankshaft rotation 405, is the solution for achieving perfect balance. It is also noteworthy that a single crankpin X-4 engine configured in this way results in having one piston 18, 28 coming to top-center for every 90° of rotation of the crankshaft - a condition which is necessary for achieving an even- firing 2-stroke 4-cylinder engine.
  • FIG. 12(e) the moment loading on the crankshaft as a result of the reciprocating masses acting on the crankpin as it moves out of alignment with the centerline of the DASY is shown.
  • This graph represents the simplest X-engine configuration and shows that the nature of the torsional loading on the crankshaft resulting from each reciprocating DASY 12 is a second-order sine wave, which for two DASYs running 90° out of phase results in perfect cancellation of the crankshaft moment loads.
  • Other X-engine configurations are multiple combinations of what is shown in FIG. 12(e).
  • 1 st order balance shaft 401 There is one crankshaft configuration with one firing order for the DASY X-4 (2-stroke) engine which is the sequence of when the cylinders reach top-center.
  • FIGS. 13(a)-(c) The DASY X-12 configuration for even-firing 4-stroke cycle is shown in FIGS. 13(a)-(c).
  • FIG. 13(a) the crankshaft 516, which has six crankpins 541, 542, 543, 544, 545, 546 is shown
  • FIG. 13(b) is a view of the X-12 (4-stroke) crank train 500 showing the X-Y-Z coordinate system used in the balance calculation, and showing the balance shaft 501, and the crankshaft rotation direction 505 being clockwise looking down the z-axis, and the balance shaft rotation direction 506 being counter-clockwise.
  • FIG. 13(a) the crankshaft 516, which has six crankpins 541, 542, 543, 544, 545, 546 is shown
  • FIG. 13(b) is a view of the X-12 (4-stroke) crank train 500 showing the X-Y-Z coordinate system used in the balance calculation, and showing the balance shaft 501, and the crankshaft rotation
  • crankpins 541, 542, 543, 544, 545, 546 are arranged in three "split-pin" pairs, which are adjacent crankpins with angular offset relative to each other.
  • the split-pin angle 577 is 30°, as shown in FIG. 13(c), makes two groups of three crankpins - 541, 543, 545 and 542, 544, 546 - each having a 120° mutual relative angle in between them as shown by feature 575, which is the angle 120° between crankpins 541 and 545.
  • crankpins 541, 543, 545 are each coupled to a single DASY 12, which moves on axes parallel to the x-axis
  • crankpins 542, 544, 546 are each coupled to a single DASY 12, which moves on axes parallel to the y-axis.
  • the upper "split-pin" crankpin 32 pair are engaged thusly: crankpin 541 has one reciprocating DASY assembly 12 coupled to it to engage cylinders 80 on banks 151 and 153, which are numbered cylinders #1 and #3, respectively.
  • Crankpin 542 has one reciprocating DASY assembly 12 coupled to it to engage cylinders 80 on banks 152 and 154, which are numbered cylinders #2 and #4, respectively.
  • the lower two split- pin crankpin pairs 543, 544 and 545, 546 engage the two lower X-4 groups in the same way as this for cylinders #5-#12.
  • the engine bottom end assembly is similar to that shown in FIG. 5(d), except that there are three cylinders 80 on each of four banks of cylinders 151, 152, 153, 154.
  • crankshaft being balanced for forces, but generating a rotating couple as the crankshaft rotates.
  • this configuration requires a single counter-rotating l st -order moment balance shaft 501 working in conjunction with the rotating moment generated by the crankshaft 516 in order to cancel out all moments and achieve perfect balance.
  • FIG 14(e) the moment loading on the crankshaft as a result of the reciprocating masses acting on the crankpins as they move out of alignment with the centerline of the DASYs 33 is shown.
  • the DASY X-12 (4-stroke) is perfectly balanced using a single l st ⁇ order balance shaft 501. While this embodiment defines one crankshaft configuration, there are four crankshaft configurations which can achieve even-firing 4-stroke cycle with perfect balance using a single balance shaft out of a total of 64 crankshaft configurations that have even-firing. There are 32 possible firing orders for each of the four crankshaft configurations for the even-fire 4-stroke X-12 with a single balance shaft and having perfect balance.
  • FIGS. 15(a)-(c) The DASY X-8 configuration for even-firing 2-stroke cycle is shown in FIGS. 15(a)-(c).
  • FIG. 15(a) the crankshaft 616, which has two crankpins 641, 642 is shown
  • FIG. 15(b) is a view of the X-8 (2-stroke) crank train 600 showing the X-Y-Z coordinate system used in the balance calculation, and showing the balance shaft 601, and the crankshaft rotation direction 605 being clockwise looking down the z-axis, and the balance shaft rotation direction 606 being counter-clockwise.
  • FIG. 15(a) the crankshaft 616, which has two crankpins 641, 642 is shown
  • FIG. 15(b) is a view of the X-8 (2-stroke) crank train 600 showing the X-Y-Z coordinate system used in the balance calculation, and showing the balance shaft 601, and the crankshaft rotation direction 605 being clockwise looking down the z-axis, and the balance shaft rotation direction 606 being
  • crankshaft 616 is a top-hidden-line view of the crankshaft 616 (without the counterweights) showing that the two crankpins 641, 642, are arranged with an angular offset 675 of 135°.
  • the engine bottom end assembly is similar to that shown in FIG. 5(d).
  • Crankpin 641 has two reciprocating DASY assemblies 12 coupled to it to engage a cylinder 80 on each of the four banks 151, 152, 153, 154, with the cylinders being numbered #1, #2, #3, #4 corresponding to the cylinder banks 151, 152, 153, 154, respectively, and the lower crankpin 642 is also engaged with two reciprocating DASY assemblies 12 and is associated with the second group of four cylinders numbered #5, #6, #7, #8.
  • This two pin crankshaft allows for an even-firing 8-cylinders for the 2-stroke cycle having one cylinder at top-center for every 45° of crankshaft rotation.
  • crankshaft rotating moment acts to cancel out the forces resulting from the reciprocating DASY assemblies 12, whereas the crankshaft rotating moment, working in conjunction with the rotating moment from the single counter- rotating l st -order moment balance shaft 601, act to cancel out all moments and achieve perfect balance.
  • FIGS. 16(b) With regards to moments about the y-axis and the x-axis, in FIGS.
  • crankshaft configuration there are four crankshaft configurations which can achieve even- firing 2-stroke cycle with perfect balance using a single balance shaft out of a total of four crankshaft configurations that have even-firing. There is one firing order for each of the four crankshaft configurations for the even- fire 2-stroke X-8 with perfect balance.
  • FIGS. 17(a)-(d) and FIGS. 18(a)-(b) The DASY X-8 configuration for even-firing 4-stroke cycle and having a 75° X-angle (unlike previous configurations discussed which have a "90° X-angle") is shown in FIGS. 17(a)-(d) and FIGS. 18(a)-(b).
  • FIG. 17(a) the crankshaft 716, which has four crankpins 741, 742, 743, 744, is shown
  • FIG. 17(b) is a top- hidden- line view of the crankshaft 716 (without the counterweights) showing that the four crankpins 741, 742, 743, 744, are arranged in two "split-pin” pairs, which are adjacent crankpins with angular offset relative to each other.
  • the split-pin angle 777 is 15°, as shown in FIG. 17(b), which makes two groups of two crankpins - 741, 743 and 742, 744 - each having a 180° opposed relative angle in between them.
  • Crankpins 741, 743 are each coupled to a single DASY 12, which moves on axes parallel to the x-axis
  • crankpins 742, 744 are each coupled to a single DASY 12, which moves on axes which are on a plane that is angle 778 (FIG. 17(c)) which is a 15° angle, offset from a plane that intersects the crankshaft axis 30 and the y-axis.
  • crankpin 741 has one reciprocating DASY assembly 12 coupled to it to engage cylinders 80 on banks 751 and 753 of engine bottom end assembly 760 as shown in FIG. 17(d) and FIG. 18(b), which are numbered cylinders #1 and #3, respectively.
  • Crankpin 742 has one reciprocating DASY assembly 12 coupled to it to engage cylinders 80 on banks 752 and 754, which are numbered cylinders #2 and #4, respectively.
  • the lower split-pin crankpin pair 743, 744 engage the lower X-4 group in the same way as this for cylinders #5-#8.
  • this X-engine configuration has an angle 775 which is a 75° angle between adjacent cylinder banks 751, 752 and 753, 754, and the other two sets of adjacent cylinder banks 752, 753 and 754, 751 are separated by angle 776 which is 105°.
  • crankshaft and the four reciprocating DASY assemblies 12 being balanced for forces as the crankshaft 716 rotates, but generating a rotating couple.
  • the solution for achieving perfect balance is by having a counter-rotating l st -order moment balance shaft 701 in order to cancel out all moments and achieve perfect balance.
  • the DASY X-12 configuration for even-firing 4-stroke cycle and having a 75° X-angle has a crankshaft 816 shown in FIG. 18(c) and FIG. 18(d) which is a top-hidden-line view of the crankshaft 816 (without the counterweights).
  • the engine bottom end assembly is the same as the 75° X-8 configuration 760 shown in FIG. 17(d) and FIG. 18(b) except there are three cylinders 80 on each cylinder bank 751-754, and the crank train assembly is similar to 700 shown in FIG. 17(c) and FIG. 18(a) except there are six crankpins instead of four and six DASYs instead of four, and with the crankpins having different angular spacing.
  • crankpins 841, 842, 843, 844, 845, 846 are arranged in three "split-pin" pairs, which are adjacent crankpins with the split-pin angle 875 being 15°, as shown in FIG. 18(d), which makes two groups of three crankpins - 841, 843, 845 and 842, 844, 846 - with each group having a 120° mutual spacing between crankpins.
  • Crankpins 841, 843, 845 are each coupled to a single DASY 12, which moves on axes parallel to the x-axis
  • crankpins 842, 844, 846 are each coupled to a single DASY 12, which moves on axes which are on a plane that is angle 778 (FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention concerne un ensemble moteur en X (160) qui comprend quatre rangées de cylindres (151-154) se situant sur deux plans d'intersection, l'axe du vilebrequin (30) se situant sur la ligne (190) d'intersection des deux plans, et est équipé d'un système de conversion de puissance à fourches à excentrique Scotch à double action (DASY), qui couple le mouvement de va-et-vient des pistons au vilebrequin tournant pour produire un mouvement de piston sinusoïdal pur. Une série de configurations de moteur en X à DASY produisant un ordre d'allumage des cylindres par paires, pour des cycles de moteur à 2 temps et à 4 temps et d'autres cycles de moteur, permet d'obtenir un équilibre parfait du point de vue des forces et des moments de vibration, qui s'annulent tous, et toutes les configurations présentent une vibration de torsion nulle du vilebrequin résultant des masses à mouvement alternatif.
PCT/US2011/049492 2011-08-29 2011-08-29 Ensemble moteur en x équilibré WO2013032431A1 (fr)

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US13/521,312 US9051833B2 (en) 2011-08-29 2011-08-29 X-engine assembly with perfect balance
EP11752430.6A EP2751390A1 (fr) 2011-08-29 2011-08-29 Ensemble moteur en x équilibré
PCT/US2011/049492 WO2013032431A1 (fr) 2011-08-29 2011-08-29 Ensemble moteur en x équilibré

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US9051833B2 (en) 2015-06-09
US20130098335A1 (en) 2013-04-25

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